Dual-bearing reel handle attachment structure

ABSTRACT

For a round dual-bearing reel manufactured of metal, a handle attachment structure to impart a classic feel to the outward appearance of the reel unit, to prevent fishing line from getting tangled on, and debris from adhering to the outer surface of the handle. The handle attachment structure, for non-rotatively attaching a handle ( 2 ) to an end of a handle shaft ( 30 ) in which a male-threaded portion ( 30   a ) is formed, includes a handle arm ( 2   a ), a nut ( 28 ) and a retainer ( 29 ). The handle arm ( 2   a ) has an oblong hole ( 2   c ) with which the handle is mounted non-rotatively to the end of the handle shaft ( 30 ), and a non-circular accommodating recess ( 2   d ) of a predetermined depth formed around the oblong hole ( 2   c ) on an outer surface of the handle arm. The nut ( 28 ) has a polygonal nut portion ( 28 ), which is screwed to the end of the handle shaft ( 30 ). The retainer ( 29 ), which is accommodated in the accommodating recess ( 2   d ), is substantially coplanar with the outer surface of the handle arm ( 2   a ), and stops the rotation of the nut ( 28 ) by engaging with the nut portion ( 28   a ) of the nut ( 28 ).

BACKGROUND OF THE INVENTION

1. Technical Field

The present invention relates to handle attachment structures, and in particular, to dual-bearing fishing reel handle attachment structures for non-rotatively attaching the handle to the tip of an endwise-threaded handle shaft in the dual-bearing reel.

2. Description of Related Art

Among dual-bearing reels having a drag mechanism on the handle shaft, round dual-bearing reels having a metal reel body that is approximately circular when viewed from the side are known. With this type of round dual-bearing reel, the handle is attached to the end of the handle shaft and is usually fastened on by a nut. A turn-stop member is attached to the nut, so as to prevent the nut from loosening when the star drag of the drag mechanism is rotated in reverse.

The handle includes a plate-shaped handle arm, which is mounted on the handle shaft, and grips attached to either one or both ends of the handle arm. The turn-stop member is made of an approximately teardrop metal plate, and is mounted on a surface of the handle arm facing away from the reel unit (outer handle surface). A star-shaped engagement hole for engagement with the peripheral corners of the nut is formed in the turn-stop member. Screwing the turn-stop member fast onto the handle arm stops the nut from loosening. With this configuration, the turn-stop member protrudes slightly from the outer surface of the handle arm, and the nut protrudes outward from the turn-stop member. Furthermore, the head of the screw for holding the turn-stop member protrudes from the turn-stop member.

When the nut and the turn-stop member protrude from the handle arm, there is the problem that bait or debris tends to adhere to the protruding portion, and the fishing line gets tangled on the protruding portion.

In this regard, for dual-bearing reels that are not round, there are configurations in which the nut and the end of the handle shaft are covered smoothly by a turn-stop member made of a synthetic resin polymer. However, when a turn-stop member thus made of a synthetic polymer is used for round dual-bearing reels made of metal, the uniformity of the overall design is lost, making it difficult to impart a classic feel to the appearance.

SUMMARY OF THE INVENTION

An object of the present invention, adopted in round dual-bearing reels manufactured of metal, is to impart a classic feel to the appearance of, and moreover prevent line from getting tangled on and debris from sticking to, the outer surface of the handle.

According to a first aspect of the present invention, a dual-bearing reel handle attachment structure for non-rotatively attaching a handle to an end of a handle shaft of a dual-bearing reel, in which a threaded portion is formed on the end of the handle shaft, includes a handle arm, a nut and a turn-stop member. The handle arm has a mounting hole with which the handle is mounted non-rotatively to the end of the handle shaft, and a non-circular accommodating recess of a predetermined depth formed around the mounting hole on an outer surface of the handle arm. The nut has a polygonal outer peripheral portion and is screwed to the end of the handle shaft. The turn-stop member, which is accommodated in the accommodating recess, is substantially coplanar with the outer surface of the handle arm and stops the rotation of the nut by engaging with the outer peripheral portion of the nut.

With this handle attachment structure, a turn-stop member arranged on the outer surface of the handle arm is accommodated in an accommodating recess formed in the handle arm, and the outer surface of the handle arm and the surface of the turn-stop member are coplanar. Therefore, only the nut protrudes from the outer surface of the handle arm, so that a round dual-bearing reel made of metal with a classic design is obtained, the fishing line is prevented from becoming entangled with the outer surface of the handle, and debris is prevented from adhering to the outer surface of the handle.

According to a second aspect of the present invention, in a dual-bearing reel handle attachment structure as in the first aspect, the turn-stop member is made of a metal plate. In this case, metal, which is stronger, is used for the turn-stop member, so that the turn-stop member can be thin, and the accommodating recess can be shallow.

According to a third aspect of the present invention, in a dual-bearing reel handle attachment structure as in the first or second aspect, the perimeter of the turn-stop member conforms to the edge of the accommodating recess. In this case, the gap between the turn-stop member and the accommodating recess is small, so that less foreign matter accumulates in the gap. Also, the turn-stop member is kept from rotating in the accommodating recess, and the engagement structure with the turn-stop member is simple.

According to a fourth aspect of the present invention, in a dual-bearing reel handle attachment structure as in the third aspect, the accommodating recess has, formed surrounding the handle shaft, an approximately teardrop rim made up of a large-diameter section, a small diameter section formed in a position at a remove from the large diameter section, and a linking section that links the two in an envelope curve. In this case, a simple structure in which the turn-stop member keeps the nut from rotating and the turn-stop member itself does not rotate can be achieved on a minimal area.

In a dual-bearing reel handle attachment structure according to a fifth aspect of the present invention, in a structure as in the fourth aspect, a fastener that screws the turn-stop member in the accommodating recess fast to the handle arm is formed in a turn-stop portion corresponding to the small diameter section; and in a turn-stop portion corresponding to the large-diameter section an engagement hole is formed for engagement with the outer periphery of the nut. In this case, the turn-stop member is kept from rotating by screwing the turn-stop member into the accommodating recess.

According to a sixth aspect of the present invention, in a dual-bearing reel handle attachment structure as in the fifth aspect, the fastener includes a through-hole through which the threaded portion of a threaded member including a head portion and a threaded portion smaller than the head portion can be passed, and an accommodating portion for accommodating the head portion. In this case, while the threaded member keeps the turn-stop member from rotating, the head portion of the threaded member does not protrude from the turn-stop member, and fishing line is not so easily caught between the head portion and the turn-stop member. Therefore, entangling of the fishing line on the outer handle surface is prevented even better.

According to a seventh aspect of the present invention, in a dual-bearing reel handle attachment structure as in any of the first to sixth aspects, the nut is a metal hexagonal cap nut including a hexagonal nut portion of predetermined length, and a cap portion with a diameter that is smaller than the nut portion's diameter. Herein, the cap portion of the nut is made to cover the end of the handle shaft, and giving the shape of the cap portion a smooth convex surface prevents line from getting tangled on and debris from sticking to, the outer surface of the handle

According to an eighth aspect of the present invention, in a dual-bearing reel handle attachment structure as in the seventh aspect, the predetermined length of the nut portion is 0.8 to 1.3 times the thickness of the turn-stop member. In this case, the nut portion hardly protrudes from the turn-stop member, which reduces the likelihood of the nut portion being felt by the hands or otherwise coming in to contact with fishing line.

From the following detailed description in conjunction with the accompanying drawings, the foregoing and other objects, features, aspects and advantages of the present invention will become readily apparent to those skilled in the art.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is an oblique view of a dual-bearing reel in an embodiment of the present invention;

FIG. 2 is a lateral view of the dual-bearing reel in FIG. 1, seen from the left;

FIG. 3 is a plane sectional view of the dual-bearing reel in FIG. 1;

FIG. 4 is a bottom view of the dual-bearing reel in FIG. 1;

FIG. 5 is an oblique view of the reel body, with its left (second) side-cover shown exploded, and its right (first) side-cover pivoted down, from the reel body;

FIG. 6 is a lateral view, seen from the right as the first side-cover is open;

FIG. 7 is a transverse sectional view of the dual-bearing reel;

FIG. 8 is a vertical sectional view of the dual-bearing reel;

FIG. 9 is a front elevational view of the inside surface of the first side-cover;

FIG. 10 is a fragmentary sectional view corresponding to and enlarged from FIG. 3;

FIG. 11 is a lateral section view, shown when the second side-cover is open.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

First Embodiment

The dual-bearing reel shown in FIGS. 1 to 3, which is an embodiment of the present invention, is a round dual-bearing reel for bait-casting. This reel includes a reel body 1, a spool-cranking handle 2, and a star drag 3 for adjusting drag. The handle 2 is disposed on one side of the reel body 1. The start drag 3 is disposed on the same side of the reel body 1 as the handle 2.

Configuration of the Handle

The handle 2 is of the double-handle type and has a plate-shaped arm portion 2 a and grips 2 b that are attached rotatively to both ends of the arm portion 2 a. As shown in FIG. 3, the arm portion 2 a is mounted non-rotatively to the near end of a handle shaft 30, and is fastened to the handle shaft 30 with a nut 28. The near end of the handle shaft 30 is smaller in diameter than the rest, and an externally threaded portion 30 a and parallel beveled portions 30 b are formed on its outer peripheral surface. Screwing the nut 28 onto the externally threaded portion 30 a fastens the arm portion 2 a to the handle shaft 30.

As shown in FIG. 2, an oblong hole 2 c is formed in the arm portion 2 a where it is mounted onto the handle shaft 30. The arm portion 2 a is engaged non-rotatively with the handle shaft 30 by engaging the beveled portions 30 b into this oblong hole 2 c. A substantially teardrop accommodating recess 2 d, configured as an envelope curve linking both a large-diameter section and a small-diameter section that is placed apart from the large-diameter section, is formed surrounding the oblong hole 2 c.

The nut 28 is kept from rotating with a retainer 29, which is fitted into the accommodating recess 2 d of the arm portion 2 a. The nut 28 is a hexagonal cap nut having a hexagonally formed nut portion 28 a of predetermined length and a frustum-shaped cap portion 28 b whose diameter is smaller than that of the nut portion 28 a and tapers gradually. The axial length of the nut portion 28 a (predetermined length) is 0.8 to 1.3 times the thickness of the retainer 29.

By setting the axial length of the nut portion 28 in this range, the nut portion 28 a hardly protrudes from the outer surface of the retainer 29, and the likelihood of the nut portion being felt by the hands or otherwise coming in to contact with fishing line is reduced. The configuration of the cap portion 28 b rounds the end smooth, making it unlikely to get caught on fishing line.

The retainer 29 is an approximately teardrop, plate-shaped member made of metal, such as a piece of stainless steel, whose outer form follows the rim of the accommodating recess 2 d that is configured as the envelope curve linking both the large-diameter section and the small-diameter section placed apart from the large-diameter section. The thickness of the retainer 29 is substantially equal to the depth of the accommodating recess 2 d. As a result, the retainer 29 is substantially coplanar with the outside surface of the arm portion 2 a. A star-shaped engagement hole 29 a with twelve corners is formed in the portion of the retainer 29 that corresponds to the large-diameter section and interlocks with the outer corners of the nut portion 28 a. A small screw 29 b having a threaded portion and a head for preventing it from falling off and for limiting its rotation is mounted in a through hole 29 d, which is formed in the portion that corresponds to the small-diameter section. With this small screw 29 b, the retainer 29 is fastened to the arm portion 2 a. In the portion of the retainer 29 where the small screw is mounted, an accommodating portion or a circular mounting recess 29 c is formed, so that the head of the small screw 29 b does not protrude from the outer surface of the arm portion 2 a. Thus, the fishing line is unlikely to get caught on or be cut into by the retainer 29 and the small screw 29 b, because they do not protrude from the arm portion 2 a.

Configuration of the Reel Unit

The reel body 1 is made of metal, such as an aluminum alloy or a magnesium alloy for example, and includes a frame 5, and a first side-cover 6 and a second side-cover 7 attached to the two sides of the frame 5. A spool 12 for winding fishing line is detachably fitted within the reel body 1, wherein it is allowed to rotate on a spool shaft 20 (see FIG. 3). When seen from the outside in the spool shaft direction, the first side-cover 6 is circular, and the second side-cover 7 is configured as staggered disks, with their two outer circumferences intersecting one another.

As shown in FIG. 3, the spool 12, a clutch lever 17 and a level wind mechanism 18 are disposed inside the frame 5. The clutch lever 17 functions as a thumb rest when pitching. The level wind mechanism 18 is for uniformly winding fishing line around the spool 12. A gear mechanism 19, a clutch mechanism 21, a clutch control mechanism 22, a drag mechanism 23, and a casting control mechanism 24 are disposed in the space between the frame 5 and the second side-cover 7. The gear mechanism 19 transmits rotational force from the handle 2 to the spool 12 and the level wind mechanism 18. The clutch control mechanism 22 controls the clutch mechanism 21 in response to the operation of the clutch lever 17. The drag mechanism 23 dampens the spool 12. The casting control mechanism 24 adjusts the resistance that develops when the spool 12 rotates. Also, a centrifugal braking mechanism 25 for preventing backlash when casting the fishing line is disposed between the frame 5 and the first side-cover 6.

Configuration of the Frame

As shown in FIGS. 3 to 6, the frame 5 includes a pair of side-plates 8 and 9 disposed in opposition to each other at a predetermined spacing, and upper and lower connecting portions 10 a and 10 b connecting the side-plates 8 and 9 into one unit. Of the pair of side-plates 8 and 9, the side-plate 9 is on the side where the handle 2 is attached, that is, on the right side in FIG. 3. Together with the second side-cover 7, it forms part of a first cylindrical portion 11 a and a second cylindrical portion 11 b that has substantially the same diameter as the first cylindrical portion 11 a. Inside the first cylindrical portion 11 a, there is a columnar first space, and inside the second cylindrical portion 11 b, there is a second space that communicates interiorly with the first space. The outer circumference of the second cylindrical portion 11 b, which protrudes in the spool shaft direction from the first cylindrical portion 11 a, is disposed staggered downward towards the front, so that it intersects with the outer circumference of the first cylindrical portion 11 a. Furthermore, the outer peripheral surfaces of the first cylindrical portion 11 a and the second cylindrical portion 11 b partially overlap in the spool shaft direction.

The side-plate 8, which is disposed on the side opposite to where the handle is attached, that is, on the left side in FIG. 3, is a flat and cylindrical element with a base, having a space inside that is circular when seen in spool shaft direction. A circular opening 8 a for attaching and detaching the spool 12 is formed slightly above the center of the side-plate 8. An internally threaded portion 8 b is formed on the inner peripheral surface of the opening 8 a. A spool support portion 13, which supports the left end of the spool shaft 20 serving as the rotation shaft for the spool 12, is provided detachably at the internally threaded portion 8 b.

As shown in FIG. 1, 3 and 6, the spool support portion 13 includes a ring portion 14, a cylindrical bearing portion 15 having a base, and a convex handle portion 16. The ring portion 14 is installed detachably in the opening 8 a. The bearing portion 15 is arranged concentrically to the ring portion 14 to the inner side of the ring portion 14. The convex handle portion 16 connects the ring portion 14 with the bearing portion 15 and is for turning the spool support portion 13. These portions are formed in one piece of plastic or metal.

On the outer peripheral surface of the ring portion 14, an externally threaded portion 14 a is formed, which can be screwed into the internally threaded portion 8 b formed in the opening 8 a. A brake liner 68 of a centrifugal braking mechanism 25 is fastened to the inner peripheral surface of the ring portion 14.

A bearing 26 b for rotatively supporting one end of the spool shaft 20 is provided at the inner peripheral surface of the bearing portion 15. A friction plate 51 of the casting control mechanism 24 is mounted on its bottom.

Curved convexly outward in axial direction, the convex handle portion 16 connects the ring portion 14 with the bearing portion 15 and is disposed along a diameter direction of these. As a result, openings 16 a are formed on both sides of the convex handle portion 16. It is possible to see the side of the spool 12 and to introduce one's fingertips through these openings 16 a.

As shown in FIG. 5, the right side-plate 9 includes a flat cylindrical mounting section 9 a having a base and a protruding section 9 b. The mounting section 9 a has the same diameter as the side-plate 8. The protruding section 9 b is formed on the edge of the mounting section 9 a staggered diagonally downward to the front, such that its outer circumference intersects with the outer circumference of the mounting section 9 a. The protruding section 9 b is formed as a crescent-shaped circular arc. A boss 9 c supporting a pinion gear 32, described below, is formed in the base of the mounting section 9 a. Two upright positioning pins 9 d and 9 e for positioning the second side-cover 7 are provided on both sides of the boss 9 c. On the tips of the positioning pins 9 d and 9 e, small-diameter nibs with are formed, and the side-plate 9 is positioned with respect the second side-cover 7 by inserting the nibs into locating holes 7 e and 7 f formed in the second cover 7.

Furthermore, diagonally below of the boss 9 c, a boss 9 f supporting the base end of the handle shaft 30 is formed. The boss 9 f is formed in the section in which the outer circumference of the mounting section 9 a is coincident with the outer circumference of the protruding section 9 b. Moreover, a slightly indented, fan-shaped guide portion 9 g for guiding the clutch plate 55 of the clutch control mechanism is formed between the boss 9 c and the positioning pin 9 e. An inner/outer circumferentially penetrating cutout 9 i for locating a gear member 63 (see FIG. 11) of the level wind mechanism 25 is formed extending from the rim on the front side of the mounting section 9 a to the base of the protruding section 9 b. A cover member 41 that is curved in a circular arc to follow the outer edge of the gear member 63 a is detachably fitted on to shut this cut-out portion 9 i. On the protruding section 9 b, a rim 9 h is formed that is curved in a circular arc to follow the outer edge of the section crescent-shaped from the portion that slants diagonally downward towards the front. The rim 9 h is formed in the protruding section 9 b up to the positions where the two outer circumferences intersect.

The upper connecting portion is arranged in the same plane as the perimeter of the side-plates 8 and 9, whereas a pair of front and rear connecting portions 10 b are formed inwardly from the perimeter. As shown in FIGS. 4 and 7, extending front to rear, an oblong rod-mounting leg 4 made of metal, such as an aluminum alloy for example, for mounting the reel to a fishing-rod is riveted to the lower connecting portions 10 b. On the rear surface of the rod-mounting leg 4, multiple anti-slipping portions 4 a made of circular concavities are formed, especially at both ends. These anti-slipping portions 4 a are made by press-forming, and are also provided to enhance the flexural rigidity of the rod-mounting leg 4 due to the work-hardening effect.

Configuration of the First Side-cover

As shown in FIGS. 6, 8 and 9, the first side-cover 6 can be opened or closed on the frame 5, and is mounted pivotally to the side-plate 8 to make it possible to attach and detach the spool 12. The first side-cover 6 can be pivoted from the closed position shown in FIGS. 3 and 4 to the open position shown in FIGS. 1 and 6. The first side-cover 6 includes a disk-shaped cover 33 covering the outer side of the side-plate 8, a pivot shaft 34 for pivotally supporting the cover 33, and a coil spring 35 urging the cover 33 away from the side-plate 8.

The cover 33 is made of a piece of metal that is slightly curved convexly outward so as to cover the side-plate 8. In order to enhance its appearance and to make it lighter, its peripheral portion is provided with multiple round holes 33 b of varying diameter, spaced apart in the circumferential direction and the radial direction. On the inner surface near the periphery of the cover 33, a threaded hole 33 a for attaching the pivot shaft 34 is formed. Around the threaded hole 33 a, a boss 33 c is formed protruding from the outer edge of the threaded hole 33 a toward the center. At the boundary with the bottom of the boss 33 c, an engagement portion 33 d is cut out linearly and substantially along the circumferential direction. Moreover, an inwardly protruding attaching portion 33 e (see FIG. 3) is formed on the inner surface of the cover 33, slightly deviating from its center. When the cover 33 is fitted to the side-plate 8, the attaching portion 33 e is located at a position near the convex handle portion 16 of the spool support portion 13 where it can abut against the spool support portion 13, so that the spool support portion 13 is not loosened by rotation in a loosening direction.

A sealing member 42 for preventing the intrusion of debris or liquids through the round holes 33 b is attached to the inner surface of the cover 33. The sealing member 42 is made of a synthetic resin, such as ABS (acrylonitrile butadiene styrene) resin, and is translucent so that its inside can be seen. As shown in FIG. 9, the sealing member 42 is curved convexly outward in adaptation to the curving of the cover 33, and its outer diameter follows the inner edge of the cover 33. At the portion of the sealing member 42 that runs along the boss 33 c, a recess 42 a is formed, which interlocks with the engagement portion 33 d. Also, a cylindrical portion 42 b covering the attaching portion 33 e is provided on the inner surface of the sealing member 42. Penetrating this cylindrical portion 42 b, a screw 42 c is screwed into the attaching portion 33 e, and the sealing member 42 is fastened to the rear surface of the first side-cover 6 with the recess 42 a and the cylindrical portion 42 b. That is to say, to attach the sealing member 42 to the first side-cover 6, the cylindrical portion 42 b is slipped onto the attaching portion 33 e, after fitting the recess 42 a against the engagement portion 33 d. Then, the screw 42 c is screwed into the attaching portion 33 e to fasten the sealing member 42 to the inner surface of the first side-cover 6.

As shown in FIG. 10, a threaded portion 34 a that is screwed into the threaded hole 33 a is formed on the tip of the pivot shaft 34. A tool engagement portion 34 b with a larger diameter is formed adjacent to the threaded portion 34 a. The threaded portion 34 a is screwed into the cover 33, thereby fastening the pivot shaft 34 to the cover 33.

A pipe member 36 penetrating the side-plate 8 is arranged concentrically around the pivot shaft 34. The tip of the pivot shaft 34 is supported rotatively by the pipe member 36. The base end of the pivot shaft 34 is supported rotatively by the side-plate 9, and protrudes outward beyond the second cover 7. The pipe member 36 supports the pivot shaft 34 not only rotatively, but also such that the pivot shaft 34 cannot shift axially. A large-diameter section 36 a is formed on the tip of the pipe member 36, and an O-ring 37 for restricting the pivoting speed is mounted inside this large diameter potion 36 a.

Between the large-diameter section 36 a and the side-plate 8, a compressed coil spring 35 is mounted around the pivot shaft 34. Parallel cut-away portions 36 b are formed in the outer peripheral surface of the pipe member 36, except for the portion of the large diameter potion 36 a. A support member 38 having an oval hole 38 a for supporting the cut-away portions 36 b non-rotatively but movably in the axial direction is screwed to the side-plate 8. A check disk 39 for checking the axial shifting of the pivot shaft 34 is fastened with a snap ring 39 a to the base end of the pipe member 36. By retaining the pipe member 36 between this check disk 39 and the tool engagement portion 34 b, the pivot shaft 34 cannot be shifted axially with respect to the pipe member 36. Also, when the first side-cover 6 is opened, the check disk 39 abuts against the side-plate 8, thus determining its axial position. Thus, the first side-cover 6 is mounted, pivotally and movably in the axial direction over a certain distance, to the side-plate 8, and can be opened and closed without the side-plate 8 falling off.

A threaded portion 34 c is formed on the base end of the pivot shaft 34. The threaded portion 34 c is screwed into an attach/detach nut 40, which is an operating element for opening and closing the first side-cover 6. The attach/detach nut 40 is mounted to the second side-cover 7 rotatively but immovably with respect to the axial direction. When the threaded portion 34 c is released from the attach/detach nut 40 by turning the attach/detach nut 40 counterclockwise, the pivot shaft 34 is urged by the coil spring 35 to the left in FIG. 4. Thereby, the cover 33, too, shifts to the left and the first side-cover 6 opens. As the first side-cover 6 opens, it pivots due to its own weight. The pivoting speed is adjusted to an appropriate speed with the O-ring 37.

Configuration of the Second Side-cover

As shown in FIGS. 2 to 5, the second side-cover 7 has a lateral surface shaped like two staggered, intersecting circles that are identical with those of the side-plate 9. The second side-cover 7 is fasted to the side-plate 9 with, for example, three screws. The second side-cover 7 includes a mounting portion 7 c and a protruding portion 7 d. Following the protruding section 9 b of the side-plate 9, the shape of the mounting portion 7 c is that of a flat cylinder with a base, and the mounting portion 7 c has the same diameter as the protruding section 9 b. The crescent-shaped protruding portion 7 d forms an arc that is disposed staggered diagonally to the rear above the edge of the mounting portion 7 c opposing the mounting section 9 a of the side-plate 9. A cylindrical boss 7 a for supporting the handle shaft 30 and a cylindrical boss 7 b for supporting the spool shaft 20 are attached to the base portion of the mounting portion 7 c, spaced apart and protruding outward. The boss 7 a is disposed coaxially with the boss 9 f formed on the side-plate 9, and the boss 7 b is disposed coaxially with the boss 9 c. A locating hole 7 e for positioning the second side-cover 7 is formed to the front of the boss 7 b. Furthermore, a knob hole 7 g, which rotatively supports the attach/detach nut 40 for opening and closing the first side-cover 6, is formed behind the boss 7 a.

On the protruding member 7 d, a rim 7 h is formed that is curved in a circular arc following the outer edge of the section crescent-shaped from the portion that slants diagonally upward towards the rear. The rim 7 h is disposed concentrically with the mounting section 9 a of the side-plate 9, and is joined to the rim 9 h of the protruding section 9 b in the involute form. The configuration thus realizes a construction in which the outer peripheral surfaces (rims 9 h and 7 h) of the two cylindrical portions 11 a and 11 b overlap in the spool axial direction. The rims 9 h and 7 h are configured respectively as circular arcs, and are therefore readily machined.

A locating hole 7 f is formed in a position on the protruding portion 7 d astride the boss 7 b opposite the locating hole 7 e. As mentioned above, the positioning plate 9 is positioned with respect to the second side-cover 7 by inserting the nibs of the upright positioning pins 9 d and 9 b provided on the side-plate 9 into the locating holes 7 e and 7 f, and the bosses 9 c, and 9 f are centered and disposed coaxially with the bosses 7 b and 7 a.

In the thus configured reel body 1, the side-plate 9 with the second side-cover 7 forms two cylindrical portions 11 a and 11 b, interiorly having respective columnar spaces and staggered such that the outer circumferences of the two intersect. Therefore, by configuring the second cylindrical portion 11 b as a protruding portion therein that projects outward, the outer peripheral surfaces are readily machined, even wherein a protruding portion is furnished to enhance the rotational efficiency. This serves to improve the style and decorativeness in the outward appearance of the reel body in the dual-bearing reel having a protruding portion.

Configuration of the Spool

As shown in FIG. 3, the spool 12 has saucer-shaped flange portions 12 a on both ends and a cylindrical spool body 12 b between the two flange portions 12 a. The spool 12 also has a cylindrical boss 12 c, formed in one piece with it at substantially the center with respect to the axial direction on the inner side of the spool body 12 b. The spool 12 is fixed non-rotatively, for example by serration coupling, to the spool shaft 20 penetrating the boss 12 c. The fixing is not limited to serration coupling, and other coupling methods such as key coupling or spline coupling can be employed as well.

The spool shaft 20 penetrates the side-plates 9 and extends beyond the second side-cover 7. This end of the spool shaft 20 is supported rotatively with a bearing 26 a at the boss 7 b, which is provided at the second side-cover 7. The other end of the spool shaft 20 is supported rotatively with the bearing 26 b as described above.

The right end of the large-diameter section 20 a of the spool shaft 20 is disposed at a portion where the side-plate 9 is pierced, and an engaging pin 20 b, which is part of the clutch mechanism 21, is fixed in the spool shaft 20 at this place. The engaging pin 20 b pierces the large-diameter section 20 a through its diameter and protrudes from both sides in radial direction.

Configuration of Other Elements

As shown in FIG. 1, the clutch lever 17 is disposed at the rear end of the pair of side-plates 8 and 9 behind the spool 12. The clutch lever 17 slides vertically between the side-plates 8 and 9. On the side of the clutch lever 17 where the handle is mounted, an engagement shaft 17 a, which is formed in one piece with the clutch lever 7, pierces the side-plate 9. The engagement shaft 17 a is engaged with the clutch control mechanism 22.

As shown in FIG. 3 and 7, the level wind mechanism 18 is disposed between the two side-plates 8 and 9 in front of the spool 12. The level wind mechanism 18 includes a threaded shaft 46 on whose outer peripheral surface intersecting helical grooves 46 are formed, and a fishing line guide portion 47, which can be shifted back and forth on the threaded shaft 46 in the spool shaft direction. The two ends of the threaded shaft 46 are supported rotatively by shaft support portions 48 and 49 provided at the side-plates 8 and 9. In FIG. 3, the left end of the threaded shaft 46 is held by an E-shaped retaining ring 50. The gear member 63 a is attached to the right side of the threaded shaft 46 in FIG. 3. The gear member 63 a meshes with a gear member 63 b that is attached non-rotatively to the handle shaft 30. With this configuration, the threaded shaft 46 is linked to and rotated by a rotation of the handle shaft 30 in the direction taking up the line.

As shown in FIG. 7, the fishing line guide portion 47 is disposed around the threaded shaft 46 and is guided in the direction of the spool shaft 20 by a pipe member 53 and a guide shaft 54. A portion of the pipe member 53 is cut away over its entire axial length. The guide shaft 54 is disposed above the threaded shaft 46. An engagement member 47 a, which engages with the helical grooves 46 a, is mounted rotatively on the fishing line guide portion 47 and is moved back and forth in the spool shaft direction by the rotation of the spool shaft 46. An oval guide ring 47 b, through which the fishing line is passed, is provided on the upper end of the fishing line guide portion 47. The guide ring 47 b can be made of a hard ceramic material such as SiC.

The pipe member 53 interlocks with the shaft support portions 48 and 49. The guide shaft 54 is fixed to the side-plates 8 and 9 and the end of the guide shaft 54 at the side-plate 9 protrudes further toward the side-cover 7. As shown in FIG. 11, the shaft support portion 49 is substantially tear-shaped. It supports the threaded shaft 46 rotatively at a portion where its diameter is large, and is pierced by the guide shaft 54 at a portion where its diameter is small, keeping the shaft support portion 49 from rotating.

As shown in FIG. 3, the gear mechanism 19 includes a handle shaft 30, a main gear 31 fixed to the handle shaft 30, and a cylindrical pinion gear 32 meshing with the main gear 31. The handle shaft 30 is supported rotatively by the boss 9 f and the boss 7 a, and a roller type one-way clutch 86 and a pawl type one-way clutch 87 prevent the handle shaft 30 from rotating in the direction unwinding the line (reverse rotation).

The one-way clutch 87 is provided between the boss 7 a and the handle shaft 30. As shown in FIG. 11, the one-way clutch 87 includes a ratchet gear 88 and a ratchet pawl 89. The ratchet gear 88 is mounted non-rotatively to the handle shaft 30 between the main gear 31 and the gear member 63 b. The ratchet pawl 89 can pivot around the positioning pin 9 d. Substantially parallelogram-shaped ratchet teeth 88 a protrude at certain intervals in the circumferential direction on the periphery of the ratchet gear 88. The ratchet pawl 89 keeps the handle shaft 30 from rotating in a direction unwinding the line by engaging with the ratchet teeth 88 a. The tip of the ratchet pawl 89 is provided with control pieces 89 a flanking the ratchet gear 88 on both sides. The control pieces 89 a keep the ratchet pawl 89 close to the ratchet gear 88 during a rotation in the direction that winds up the line and separate the ratchet pawl 89 from the ratchet gear 88 during a rotation in the direction that unwinds the line. When the ratchet pawl 89 separates from the ratchet gear 88, the ratchet pawl 89 abuts the guide shaft 54 to prevent the ratchet pawl 89 from separating too much.

The main gear 31 is mounted rotatively on the handle shaft 30, and is coupled to the handle shaft 30 via the drag mechanism 23.

As shown in FIG. 3, the pinion gear 32 extends from outside of the side-plate 9 to the inside thereof. The pinion gear 32 is cylindrical and is pierced by the spool shaft 20, on which it is mounted movably in the axial direction. A bearing 27 in the side-plate 9 supports the left side of the pinion gear 32 in FIG. 3 rotatively and movably in the axial direction. A meshing groove 32 a meshing with the engagement pin 20 b is formed at the left end of the pinion gear 32 in FIG. 3. The meshing groove 32 a and the engagement pin 20 b form the clutch mechanism 21. A center portion of the pinion gear 32 is provided with a constricted portion 32 b, and the right end of the pinion gear 32 is provided with a gear portion 32 c meshing with the main gear 31.

As shown in FIG. 11, the clutch control mechanism 22 includes a clutch plate 55, a clutch cam 56, and a clutch yoke 57. The clutch plate 55 is engaged with the engagement shaft 17 a. The clutch cam 56 is engaged with the clutch plate 55 and rotates around the spool shaft 20. The clutch cam 56 moves the clutch yoke 57 in the direction of the spool shaft 20. The clutch control mechanism 22 also includes a clutch return mechanism 58, which clutches the clutch mechanism 21 on when the spool 12 rotates in the direction winding up the line.

The clutch plate 55 is an arcuate plate-shaped member and is guided in the rotation direction by the guiding portion 9 g formed in the side-plate 9. A collar 9 j on the positioning pin 9 e forms a gap together with the guide portion 9 g and prevents the clutch plate 55 from drifting off. One end of the clutch plate 55 extends to a position where it contacts the lower end of the engagement shaft 17 a of the clutch lever 17, so that the clutch plate 55 moves counterclockwise in FIG. 11 when the clutch lever 17 is moved downward. The other end of the clutch plate 55 interlocks with the clutch cam 56, and the clutch plate 55 and the clutch cam 56 turn in cooperation around the spool shaft 20.

The clutch cam 56 is a substantially ring-shaped plate, provided rotatively around the spool shaft 20 in the boss 9 c. A pair of oblique cam protrusions 56 a are formed in opposition to one another at positions on the outer lateral surface of the clutch cam 56, flanking the spool shaft 20. An engaging pin 56 b that is engaged with the clutch plate 55 is formed on the outer peripheral portion of the clutch cam 56. Furthermore, a coupling portion 56 c for coupling with a return pawl 59 that is part of the clutch return mechanism 58 is also formed on the outer peripheral portion of the clutch cam 56.

The clutch yoke 57 is disposed in axial opposition to the clutch cam 56. The clutch yoke 57 is movable in the direction of the spool shaft 20, guided by two upright guide shafts 60, which are provided between the side-plate 9 and the second side-cover 7, flanking the spool shaft 20. The clutch yoke 57 is urged inward in the axial direction by compressed coil springs 61 (see FIG. 3) that are provided around the guide shafts 60 between the second side-cover 7 and the clutch yoke 57. The clutch yoke 57 is provided with a semi-circularly arced engaging portion 57 a that is engaged with the constricted portion 32 b of the pinion gear 32. On a side surface opposing the clutch cam 56, the clutch yoke 57 is provided with inclined faces (not shown in the drawings) resting on the cam protrusions 56 a. When the clutch cam 56 is turned counterclockwise in FIG. 11, the protrusions 56 a lift the inclined faces and the clutch yoke 57 is moved to a clutch-off position on the right in FIG. 3. When the inclined faces are lowered from the protrusions 56 a, the clutch yoke 57 is urged back into the clutch-on position by the coil spring 61. Shifting the clutch yoke 57 moves the pinion gear 32 in the spool shaft direction, so that the clutch mechanism 21 can be switched to a clutch-off state or to clutch-on state.

The clutch return mechanism 58 includes a return pawl 59 and a toggle spring 62. The return pawl is coupled rotatively to the coupling portion 56 c of the clutch cam 56, and the toggle spring 62 biases the return pawl 59. Turning the clutch cam 57 shifts the return pawl 59, which is guided by the side-plate 9, between a position where it contacts the ratchet teeth 88 a of the ratchet gear 88 and a position where it is separated from the ratchet teeth 88 a. The toggle spring 62 holds the return pawl 59 in these two positions.

With this clutch return mechanism 58, the return pawl 59 is guided by the side-plate 9 and proceeds to a position where it is in contact with the ratchet teeth 88 a when pushing the ratchet lever 17 down puts the clutch mechanism 21 into the clutch-off state. If, in this situation, turning the handle 2 rotates the handle shaft 30 in the direction winding up the line, then the return pawl 59 is pushed by the ratchet teeth 88 a and shifts to the position away from the ratchet teeth 88 a, the ratchet cam 56 turns clockwise in FIG. 11, and the clutch mechanism 21 returns to the clutch-on state.

The casting control mechanism 24 includes a plurality of friction plates 51 and a braking cap 52. The friction plates 51 are disposed on both ends of the spool shaft 20. The braking cap 52 is for adjusting the force with which the friction plates 51 are pressed against the spool shaft 20. The left friction plate 51 is provided inside the spool support portion 13.

As shown in FIGS. 3 and 6, the centrifugal braking mechanism 25 includes a rotor 66, cylindrical sliders 67, and a brake liner 68. The rotor 66 is fixed to the spool shaft 20 so that it rotates together with the spool 12. The sliders 67 are attached to the rotor 66 at certain intervals in the circumferential direction and are movable in the radial direction. The brake liner 68 is fixed to the inner peripheral surface of the ring portion 14 and can be brought into contact with the sliders 67. The rotor 66 includes a circular plate 66 a provided around the bearing portion 15. For example six recesses 66 b are formed in the circular plate 66 a, spaced apart at intervals in the circumferential direction. In these recesses 66 b, two pairs of opposing engagement projections 70 a and 70 b are formed at a certain distance in the radial direction. The engagement projections 70 a are formed projecting towards one another at an outer periphery of the circular plate 66 a and prevent the sliders 67 from falling off. The engagement projections 70 b formed more to the inside than the engagement projections 70 a and prevent the sliders 67 from contacting the brake liner 68. Furthermore, guide shafts 69 are provided at the bottom surface of the recesses 66 b, fanning out in the radial direction. Guided by the guide shafts 69, the sliders 67 can shift back and forth thereon.

The sliders 67 are cylindrical and are provided at their inward edge portions with collars 67 a engagement with the engagement portions 70 a and 70 b. The diameter of those collars 67 a is larger than that of the other portions. When the spool 12 rotates, centrifugal forces act on the sliders 67 and bring the sliders 67 into contact with the brake liner 68, thereby braking the spool 12. If the collars 67 a are located inwardly beyond the engagement projections 70 b, then the collars 67 a abut the engagement projections 70 b when centrifugal forces are at work, so that the sliders 67 cannot be brought into contact with the brake liner 68. The braking force of the centrifugal braking mechanism 25 can then be adjusted by switching the radial positions of the sliders 67.

Attaching and Detaching the Spool To remove the spool 12 from the reel body 1, for example when backlash has caused the fishing line to become entangled with the spool 12, the first cover 6 is opened, revealing the opening 8 a in the side-plate 8.

To open the first side-cover 6, first, the attach/detach nut 40 is turned counterclockwise, and the pivot shaft 34 is detached from the attach/detach nut 40. When the pivot shaft 34 has been detached from the attach/detach nut 40, the spring force of the coil spring 35 urges the pivot shaft 34 to the left in FIG. 4, together with the first side-cover 6. Then, the first side-cover 6 pivots around the pivot shaft 34 by its own weight, and the first side-cover 6 opens. FIGS. 1 and 5 illustrate the situation when the first side-cover is open. Opening the first side-cover 6 reveals the spool support portion 13. In this situation, it is possible to insert one's fingers through the opening 16 a and switch the position of the sliders 67 of the centrifugal braking mechanism 25 in the radial direction of the spool to adjust the braking force. That is to say, when the sliders 67 are located on the inside of the engagement projections 70 b, they cannot be brought into contact with the brake liner 68, so that the braking force is weakened.

When the first side-cover 6 is open, it is possible to hold the convex handle portion 16 with thumb and index finger and turn the spool support portion 13 counterclockwise. This detaches the spool support portion 13 from the side-plate 8 and reveals the opening 8 a. In this situation, it is possible to take the spool shaft 20 and pull it out to remove the spool 12.

To insert the spool 12, the spool support portion 13 is attached to the side-plate 8 and the first side-cover 6 is closed, after the spool 12 has been placed inside the reel body 1. To do so, the cover 33 is swung by hand into its closed orientation and then pressed toward the side-plate 8. In this situation the attach/detach nut 40 is turned clockwise and screwed onto the tip of the pivot shaft 34, thereby closing the first side-cover 6 on the side-plate 8.

Operation and Function of the Reel During Actual Fishing

When casting, the clutch lever 17 is pushed down. This moves the clutch plate 55 counterclockwise in FIG. 11. This moves the clutch plate 55 on the inside of the guide portion 9 g while the positioning pin 9 e prevents it from drifting off. Moving the clutch plate 55 turns the clutch cam 56 counterclockwise, which shifts the clutch yoke 57 outward in FIG. 3 to the clutch-off position. As a result, the pinion gear 32, which is part of the clutch mechanism 21, shifts outward in the axial direction to the clutch-off state. In this clutch-off state, the spool 12 can rotate freely, and the fishing line unwinds with full momentum due to the weight of the lure when casting.

When the lure has hit the water, the handle 2 is rotated in the direction taking up the line. This causes the ratchet gear 88 to rotate in the direction taking up the line (that is, clockwise in the drawings), and the ratchet tooth 89 pivots around the positioning pin 9 away from the ratchet gear 88 due to the function of the control pieces 89 a and abuts the guide shaft 54. As a result, when taking up line, the ratchet pawl 89 does not contact the ratchet gear 88, and the clicking sound caused by the contact between the two when taking up line is averted. Also, when the ratchet gear 88 rotates in the direction for taking up line, the ratchet teeth 88 a abut against the tip of the return pawl 59 and push the return pawl 59 back. The return pawl 59 retreats beyond the dead point of the toggle spring 62, and is urged by the toggle spring 62 into a separated position. This movement turns the clutch cam 56 clockwise in FIG. 11 and the spring force of the coil spring 61 urges the clutch yoke 57 into the clutch-on position, putting the clutch mechanism 21 into the clutch-on state. Thus, the rotation of the handle 2 is transmitted to the spool 12, and the spool 12 rotates in the direction taking up line.

When the handle shaft 30 rotates in the direction taking up line, this rotation is relayed by the gear members 63 a and 63 b to the threaded shaft 46. As the threaded shaft 46 rotates, the fishing line guide portion 47 moves back and forth in the spool shaft direction, so that the fishing line is taken up uniformly by the spool 12.

Other Embodiments

(a) In the above-described embodiment, an example of a round dual-bearing reel made of metal has been explained, but the handle attachment structure of the present invention is not limited to this, and it can also be applied to round dual-bearing reels that are not made of metal or dual-bearing reels that are not round when viewed from the side.

(b) In the above-described embodiment, a small screw keeps the retainer from rotating, but it is also possible to keep the retainer from rotating with the accommodating recess itself. In this case, it is also possible to provide an engagement structure of recesses and protrusions between the nut and the retainer or the nut and the accommodating recess, so as to prevent the retainer from falling off.

(c) In the above-described embodiment, a hexagon cap nut is used for the nut, but the shape of the nut is not limited to that of hexagon cap nuts.

With the present invention, a turn-stop member arranged in the outer surface of the handle arm is accommodated in an accommodating portion formed in the handle arm, and the outer surface of the handle arm and the surface of the turn-stop member are coplanar. Therefore, only the nut protrudes from the outer surface of the handle arm, a classic design can be attained when applying this structure to a round metal dual-bearing wheel, the fishing line is prevented from becoming entangled with the outer surface of the handle, and debris is prevented from adhering to the outer surface of the handle.

While only selected embodiments have been chosen to illustrate the present invention, to those skilled in the art it will be apparent from this disclosure that various changes and modifications can be made herein without departing from the scope of the invention as defined in the appended claims. Furthermore, the foregoing description of the embodiments according to the present invention is provided for illustration only, and not for the purpose of limiting the invention as defined by the appended claims and their equivalents. 

What is claimed is:
 1. For a dual-bearing fishing reel having an endwise threaded handle shaft onto which a handle is attached, a handle attachment structure for non-rotatively attaching the handle onto the handle shaft endwise, the dual-bearing reel handle attachment structure comprising: a handle arm having a mounting hole for mounting the handle non-rotatively onto the handle shaft endwise, and a non-circular accommodating recess of a predetermined depth formed around the mounting hole in an outer surface of the handle arm; a nut having a polygonal outer periphery, the nut being screwed onto the handle shaft endwise such that a surface of the nut is exposed; a turn-stop member accommodated in the accommodating recess, a surface of the turn-stop member being substantially coplanar with an outer surface of the handle arm, the turn-stop member being for engagement with an outer periphery of the nut to stop the nut from turning with a surface of the turn-stop member being exposed.
 2. The dual-bearing reel handle attachment structure as set forth in claim 1, wherein the turn-stop member is manufactured of metal plate.
 3. The dual-bearing reel handle attachment structure as set forth in claim 1, wherein the turn-stop member in outer form conforms to the accommodating recess rim-wise.
 4. The dual-bearing reel handle attachment structure as set forth in claim 3, wherein the accommodating recess has an approximately teardrop rim consisting of a large-diameter section, a small diameter section, and a linking section, the small diameter section being formed in a position apart from the large diameter section, the linking section linking large- and small-diameter sections in an envelope curve; and the turn-stop member has the outer form of said teardrop.
 5. The dual-bearing reel handle attachment structure as set forth in claim 4, wherein: said turn-stop member includes a fastening portion formed in a portion of the turn-stop member corresponding to the small-diameter section, said fastening portion being for screwing the turn-stop member fast to the handle arm in the accommodating recess; and an engagement hole formed in a portion corresponding to the large-diameter section of the turn-stop member, said engagement hole being for engagement with the outer periphery of the nut.
 6. The dual-bearing reel handle attachment structure as set forth in claim 5, wherein the fastening portion includes: a through-hole for penetration by threads of a threaded member including a head and a threaded portion diametrically smaller than the head; and an accommodating portion for accommodating the head.
 7. The dual-bearing reel handle attachment structure as set forth in claim 1, wherein the nut is a hexagonal cap nut made of metal and includes: a hexagonal nut portion of predetermined length; and a cap portion diametrically smaller than the nut portion.
 8. The dual-bearing reel handle attachment structure as set forth in claim 7, wherein said predetermined length of the nut portion is 0.8 to 1.3 times the thickness of the turn-stop member.
 9. The dual-bearing reel handle attachment structure as set forth in claim 7, wherein the cap portion is frustum-shaped, and diameter of the cap portion tapers off gradually.
 10. A dual-bearing reel, comprising a reel body having a handle shaft; a star-drag disposed on a side of the reel body on which the handle shaft is protruding; and a handle disposed on the side of the reel body on which the star-drag is disposed, said handle including an arm portion non-rotatively mounted on an end of the handle shaft, the arm portion having formed thereon a mounting hole through which the arm portion is mounted to the handle shaft, and a non-circular accommodating recess of a predetermined depth, a nut having a polygonal outer periphery for fastening the arm portion to the handle shaft such that a surface of the nut is exposed, and a turn-stop member fitted to the accommodating recess of the armed portion, a surface of the turn-stop member being substantially coplanar with an outer surface of the handle arm, the turn-stop member being for engagement with an outer periphery of the nut to stop the nut from turning with a surface of the turn-stop member being exposed.
 11. The dual-reel bearing as set forth in claim 10, wherein the turn-stop member is manufactured of metal plate.
 12. The dual-bearing reel as set forth in claim 10, wherein the turn-stop member in outer form conforms to the accommodating recess rim-wise.
 13. The dual-bearing reel as set forth in claim 12, wherein the accommodating recess has an approximately teardrop rim consisting of a large-diameter section, a small diameter section, and a linking section, the small diameter section being formed in a position apart from the large diameter section, the linking section linking large- and small-diameter sections in an envelope curve; and the turn-stop member has the outer form of the teardrop.
 14. The dual-bearing reel as set forth in claim 13, wherein: a fastening portion for screwing the turn-stop member in the accommodating recess fast to the handle arm is formed in a portion of the turn-stop member corresponding to the small-diameter section; and an engagement hole for engagement with the outer periphery of the nut is formed in a portion corresponding to the large-diameter section of the turn-stop member.
 15. The dual-bearing reel as set forth in claim 14, wherein the fastening portion includes a through-hole for penetration by threads of a threaded member including a head and a threaded portion diametrically smaller than the head; and an accommodating portion for accommodating the head.
 16. The dual-bearing reel as set forth in claim 10, wherein the nut is a hexagonal cap nut made of metal and includes: a hexagonal nut portion of predetermined length; and a cap portion diametrically smaller than the nut portion.
 17. The dual-bearing reel as set forth in claim 16, wherein said predetermined length of the nut portion is 0.8 to 1.3 times the thickness of the turn-stop member.
 18. The dual-bearing reel as set forth in claim 16, wherein the cap portion is frustum-shaped, and diameter of the cap portion tapers off gradually. 